Compressed air installation



Jan. 14, 1947. R. PATERAS PEscARA 2,414,166

COMPRESSED AIR INSTALLATION Filed $20, 1942 s Sheets-She 1 f 3' SPEED RESPONSIVE GOVERNOR SPEED RESPONSIVE GOVERNOR 1,

SPEED Jan. 14, 1947. R. PATERAS PESCARA 2,414,156

COMPRESSED AIR INSTALLATION Filed Aug. 20, 1942 3 Sheets-Sheet 2 RESPONSIVE GOVERNOR SPEED RESPONSNE GOVERNOR mm www E swam R. PATERAS PESCARA 2,414,166

COMPRESSED AIR INSTALLATION Filed Aug. 20, 1942 3 Sheets-Sheet 3 Patented Jan. 14, 1947 COMPRESSED AIR INSTALLATION Raul Pateras Pescara, Lisbon, Portugal Application August 20, 1942, Serial No. 455,482 In France April 20, 1942 11 Claims.

My invention relates to assemblies comprising a compressed-air generator and a plant fed by same and it refers more particularly to such assemblies including an air-compressor supercharging a prime mover system.

A first object of my invention consists in using as compressed-air generator a free piston autogenerator, the exhaust gases of which are forced under pressure into the turbine element of a turbo-blower machine, and in providing means to control the output of the auto-generator in accordance with at least oneof the functional factors of the plant to which compressed air is supplied by the blower element of theturbo-blower.

Other objects of my invention will be more fully understood from the following detailed description with reference to the annexed drawings in which:

Fig. l is a diagrammatical longitudinal section of a free piston auto-generator.

Figs. 2 to 10 diagrammatically represent nine assemblies in accordance with my invention.

In Fig. 1 a free piston auto-generator I comprises a motor cylinder a, a compressor cylinder 12, preferably supercharged by a part of the compressed air delivered by the turbine-blower machine, an air cushion chamber 0, and a movable structure formed of two pistons d and e respectively cooperating with cylinders a and b. The operation may briefly be described as follows: When pistons d and e are oscillated, cylinder b forces air under pressure into the annular chamber surrounding cylinder a which operates as a two-stroke internal combustion engine with fuel injection by means of an injection pump g directcommon conduit 2 to an exhaust gas turbine 3 coupled with a rotary blower 4. The air from blower 4 is heated by a burner h and the hot gases produced are supplied to a turbine 5 formi'ng a prime mover.

The injectionpump g of the two free piston auto-generators I are controlled in known manner by means of rods f and the latter are actuated by a centrifugal speed governor 6 driven by turbine 5. 'Fuel injection to auto-generators I is thus controlled in accordance with the speed of the turbine or prime mover 5.

In the arrangement of Fig. 3, there is a pneumatic device I connected to the supply line between blower 4 and burner h responsive to the pressure of the air supply in the line for controlling rods ,f. A governor 6 controlled by'the speed of turbine 5 regulates valve u which controls burner h.

In Fig. 4 the air from blower 4 is supplied to three auto-generators 8 and the exhaust gases of the latter are fed to a turbine II). The control rods f of auto-generators I are actuated by a centrifugal speed governor .9 driven by turbine III, whereby fuel injection in auto-generators I is varied in accordance with the speed of the prime mover, as in the case of Fi 2.

In the arrangement shown in Fig. 5, the rods means permitting to vary the relative positions of the respective controlling devices, such means being inserted in the gear connecting the fuel injection controlling devices. It is thus possible to vary the quantity of fuel injected into the auxiliary auto-generators I with respect to the quantity injected into the main auto-generators 8. In the example shown in Fig. 5, there is provided an adjustable connecting rod I2 of the conventional type comprising two threaded rods with right and left hand threads co-operating with a tubular member I3 provided with right and left hand threads at its ends. The length of connecting rod I2 may thus be varied at will be rotating member I3.

Such an adjustment is more particularly used when it is desired to obtain rapidly a variation In the total output of both groups of auto-generators. Supposing the output is to be increased, the injection ratio between the main and auxiliary groups is first .redued, care being taken to maintain the total output. This output is afterwards increased and the normal injection ratio between the groups is resumed. Whenit is desired to reduce the output, the injection ratio is first increased.

In the form shown in Fig. 6, the rods of the fuel injection devices I of an auxiliary group of auto-generators (I) and of a main group (8) are jointly controlled by a governor 9 driven by turbine I0. An adjustable connection I3 is pro- .be varied.

The form shown in Fig. '7 differs from that of Fig. 6 in that the fuel injection devices of both groups are jointly controlled by a pneumatic device ll responsive to the output pressure of the main group.

The device controlling the auxiliary group of auto-generators may be responsive to a functional factor of the main group and at the same time to a functional factor of the auxiliary group, whereby the second-named factor may maintain the output of the auxiliary group to the value required for the main group.

Such a method permits the inlet pressure of the main group to remain a function of the exhaust pressure of the said group; or the working pressure of the auto-generators of the auxiliary group to remain a function of the exhaust pressure of the main group; or the speed of the turboblower to remain a function of the prime mover speed.

In the example illustrated in Fig. 8, the two functional factors are respectively the air pressure at the outlet of blower 4 and the exhaust pressure of the main group of auto-generators 8. These pressures act on opposite sides of a piston l4 connected by an appropriate gearing with the rods controlling the injection pumps. 9 of the auxiliary group I. The rods 11 controlling the injection pumps g l of the main group 8 are actuated by the centrifugal governor 9 of the prime mover I 0.

* but the two pressures acting on pistons II are respectively the exhaust pressure of the autogenerators I of the auxiliary group and the exhaust pressure of the autogenerators 8 of the main group. In this case the prime mover is a reciprocating machine I a.

In the arrangement of Fig. the turbo-blower 3, 4 associated with the auxiliary group derives a centrifugal governor l5 while the prime mover l0 drives another centrifugal governor l6. Centrifugal governors l5 and i6 respectively actuate parallel rods l1 and I8 axially sliding in a frame l9. There is also provided a third siidable rod parallel to rods l1 and I8, and rods l1, l8 and 20 are connected by means of a lever 2| articulated at its ends to rods 20 and I8 and at an intermediate point to rod H, such articulations being provided with play or other means permitting movements of the rods. And rod 20 is connected by an appropriate gearing with the rods controlling the injection pumps 9 of the auxiliary group I.

The position of lever 2| shown in full lines corresponds to a full load while the reduced load position is illustrated in dashed lines.

It is to be understood that the above description has been given merely by way of example to disclose practical and eflicient embodiments of my invention, but that I- do not wish to be limited thereto, ince the details may be varied within the scope of the appended claims. Especially, the device fed by the blower of the auxiliary group does not be necessarily a power plant but can be a network of. compressed air.

I claim:

1. A system comprising a rotary blower; a

a turbine driving said blower; at least one first free piston auto-generator of the internal combustion type adapted to supply exhaust gases under pressure to said turbine; at least one second free Q piston auto-generator of the internal combustion type to which compressed air is supplied by said rotary blower; a machine to which exhaust gases under pressure are supplied by said second-named auto-generator; and means responsive to a condition which varies with variation in the load on said machine and adapted to control said first-named auto-generator.

2. In a system as claimed in claim 1, said machine being a prime mover of the class including turbines and reciprocating engines.

3. In a system as claimed in claim 1, said machine being a prime mover of the class including turbines and reciprocating engines and said means being responsive to the speed of said prime mover. I

4. A system comprising a rotary blower; a turbine driving said blower; at least one first free piston auto-generator of the internal combustion typje adapted to supplyexhaust gases under pressure to said turbine; at least one second free piston auto-generator of the internal combustion type to which compressed air is supplied by said rotary blower; a machine to which exhaust gases under pressure are supplied by said second-namecl auto-generator; 'said first-named auto-generator; means to control said second-named auto-generator; and a positive connection between said first-named and second-named means.

5. In a system as claimed in claim 4, said connection being adjustable to permit of varying the ratio of control between said first-named and said second-named auto-generator.

6. A system comprising a rotary blower; a turbine driving said blower; at least one first free piston auto-generator of the internal combustion type adapted to supply exhaust gases under pressure to said turbine; at least onesecond free piston auto-generator of the internal combustion type to which compressed air is supplied by said rotary blower; a machine to which exhaust gases under pressure are supplied by said secondnamed auto-generator; means to control said first-named auto-generator; means to control said second-named auto-generator; a positive connection between said first-named and said second-named means; and means responsive to a condition which varies with variation in the load on said machine and adapted to actuate in unison said first-named and said second-named means.

7. In a system as claimed in claim 6, said machine being a prime mover of the class including turbines and reciprocating engines, and said lastnamed means being responsive to the speed of said prime mover.

8. In a system as claimed in claim 6, said lastnamed means being responsive to the pressure of the gases supplied to said machine.

9. A system which comprises a first group including a rotary blower, a turbine driving said blower, and at least one free piston auto-generator of the internal combustion type adapted to supply exhaust gases under pressure to said turbine; a second group including atleast one free piston auto-generator of the internal combustion type to which compressed air is supplied by said rotary blower and a machine to which exhaust gases under pressure are supplied by said second-named piston auto-generator; means to control the auto-generator of said first named group, said means being responsive to a condition which varies with variation in the load on said second-named group and also to a condimeans to control U tion which varies with variation in the load on said first-named group; and means to control said second group.

11. A power plant which comprises a first group includinga rotary blower, a turbine driving said blower andat least one tree piston auto-generator oi the internal combustion type adapted to supply exhaust gases under pressure to said turbine; a, second group including at least one tree 7 piston auto-generator of the internal combustion type to whichcompressed air is supplied by said rotary blower and a machine to which exhaust gases under pressure are supplied by said second-named free piston auto-generator; and

' means to control the tree piston auto-generator of said first group, said means being responsive to a condition which varies with variations in the load on said first group and also to a condition which varies with variation in the load on said machine.

RAUL PA'I'ERAS PESCARA. 

